Dehumidifying Cooling Device for District Heating

ABSTRACT

Disclosed is a dehumidifying cooling device for district heating which comprises; a case having a first partition to divide the interior of the case into a wet channel and a dry channel and a second partition to divided the wet channel into a first wet channel and a second wet channel, a sensible heat exchanger to heat exchange the outside air in the first wet channel with the outside air in the second wet channel, a heating coil for raising the temperature of the outside air in the second wet channel, a rotatable de humidifying wheel for adsorbing and removing moisture contained in the circulated air within the dry channel, and a regenerative-evaporative cooler for cooling the circulated air in the dry channel. With this configuration, the device can carry out an air cooling operation by use of hot water supplied by district heating systems and gas or oil boilers installed in individual households, thereby achieving a reduced device size via the implementation of the cooling operation under the atmospheric pressure state and reducing manufacturing costs by virtue of a simplified system configuration.

TECHNICAL FIELD

The present invention relates to a dehumidifying cooling device fordistrict heating, and more particularly, to a dehumidifying coolingdevice for district heating which can carry out an air cooling operationby use of hot water supplied by large-scale or small-scale districtheating systems and gas or oil boilers installed in individualhouseholds.

BACKGROUND ART

There is spreading a prospect that the recent high oil price situationis not a temporary problem, but is continuously maintained and fixed.Thereby, main energy consuming countries of the world increasingly takea great effort for securing stable energy resources. With theeffectuation of the Tokyo protocol dealing with a reduction in thedischarge of greenhouse gas for the sake of preventing global warming,it will be expected that an international pressure about the use limitof fossil energy, the criterion of energy efficiency, etc. will bestrengthened.

According to the published energy report, the amount of energy consumedin domestic and business fields of Korean in 2003 is approximately 55millions TOE a year, and occupies 25.2% of the total nationalconsumption energy. This rate also corresponds to 41.9% on the basis ofelectricity. For the past four years, the energy consumption of domesticand business fields shows an average annual rate of increase of 5.3%,whereas the consumption of electricity shows an average annual rate ofincrease of 12%. Accordingly, it will be appreciated that theconsumption of electricity particularly has a rapid increase. Estimatingon the basis of a variation in the monthly energy consumption ofresidential buildings and sample survey results about non-residentialbuildings as the subject of energy controlment, it is analyzed that 50%of the energy consumption of residential buildings and 47% of the energyconsumption of business buildings are used for air conditioning. Inconclusion, of the energy consumption of buildings, energy required forair conditioning occupies 13% of the national total energy consumptionof Korea.

Accordingly, to guarantee the efficient use of energy and the continuousdevelopment of energy industry while observing related internationalagreements, it is necessary to improve the use efficiency of energy forair conditioning in domestic and business fields. From this viewpoint,there is put in force a so-called collective-energy industry in whichthermal energy and electricity, generated from energy generationfacilities concentrated on a specific place for improving the useefficiency of energy in domestic and business fields, are suppliedcollectively to a plurality of users in residential and business areas.It is reported that the collective-energy industry utilizes waste heatoccurred during power generation as a heating source for space heatingand hot water heating, thereby achieving not only a reduction of energyby approximately 20 to 30% by virtue of an improved use efficiency ofenergy, but also an improvement of air environment by approximately 30to 40% by virtue of a reduction usage of fuel and intensiveenvironmental managements. The collective-energy industry is evaluatedas an effective industry capable of dealing with related internationalenvironmental restrictions including a climatic change convention, etc.In the affirmative evaluation's debt, in Korea, approximately 1.2million families share in the benefits of district heating in 2003, andin particular, 85% of supplied energy is generated by combined heat andpower generation. Korea has a plan to expand the propagation range ofdistrict heating to 2 million families by 2010.

In the combined heat and power generation, namely, cogeneration, thegeneration ratio of electricity to heat is fixed at 3:5. Therefore, itis important to keep the ratio of electricity to heat at an appropriatelevel for maximizing the effect of the collective-energy industry. InKorea, the above mentioned generation ratio can be fulfilled in winter,but the summer of Korea has an increased electricity load for aircooling and substantially no heat load. As a result, the operation rateof distinct heating in summer decreases to less than 10%, and thiscauses a deterioration in the economical efficiency of cogeneration.Actually, no generation results reported between June and September in2003.

To improve the operation rate of collective-energy generation facilitiesfor sufficiently utilizing the effects of the industry, excavating thedemand of heat in summer is necessary, and in particular, developmentand propagation of a technology for supplying cooling energy usingdistinct heating facilities is necessary.

In one example of the above described cooling energy supply technology,an absorption chiller is installed to a receptor, such as a large-scalebuilding, etc. such that the chiller performs a central coolingoperation using energy delivered from distinct heating facilities.

The absorption chiller is designed to chill water flowing in a pipe byuse of heat generated during the evaporation of a liquid-phaserefrigerant and condense the evaporated gas-phase refrigerant for thereuse thereof.

DISCLOSURE Technical Problem

However, despite of various researches and developments for improvingthe performance thereof, the absorption chiller has a limit in theimprovement of performance due to a low temperature of a heating source.In addition, the absorption chiller has an uneconomical high waterreturn temperature because it cannot use water having a temperature of80° C. or less, and suffers from a little difference between thetemperature of supplied water and the temperature of water to bereturned.

When the absorption chiller is installed to an apartment, etc. occupyingthe most part of district heating, so as to carry out a central coolingoperation, there is a problem in that cold water pipes have to beadditionally installed regardless of hot water supply pipes.

Therefore, the present invention has been made in view of the aboveproblems, and it is an object of the present invention to provide adehumidifying cooling device for district heating which can carry out anair cooling operation by use of hot water supplied by large-scale orsmall-scale district heating systems and gas or oil boilers installed inindividual households, thereby achieving a reduced device size via theimplementation of the cooling operation under the atmospheric pressurestate and reducing manufacturing costs by virtue of a simplified systemconfiguration.

Technical Solution

In accordance with an aspect of the present invention, the above andother objects can be accomplished by the provision of a dehumidifyingcooling device for district heating comprising: a case having a firstpartition to divide the interior of the case into a wet channel and adry channel and a second partition to divided the wet channel into afirst wet channel, and a second wet channel, the first wet channel beingprovided at one end thereof with an outside air suction hole forintroducing outside air into the first wet channel, the second wetchannel being provided at one end thereof with an exhaust hole fordischarging the outside air, the second partition being perforated witha flow hole for transferring the outside air from the first wet channelinto the second wet channel, the dry channel being provided, at one endthereof, with a circulated air suction hole for introducing circulatedair from a conditioning space into the dry channel and, at the other endthereof, with an air supply hole for supplying cooling air into theconditioning space; a sensible heat exchanger configured to rotate aboutthe second partition and serving to heat exchange the outside air,introduced into the first wet channel through the outside air suctionhole, with the outside air to be discharged from the second wet channel;a heating coil installed in the second wet channel at a position betweena rear end of the sensible heat exchanger and the flow hole and servingto raise the temperature of the outside air passing through the secondwet channel by use of heat of hot water introduced into the heatingcoil; a dehumidifying wheel configured to rotate about the firstpartition at a position between a rear end of the heating coil and theflow hole and serving to adsorb and remove moisture contained in thecirculated air within the dry channel, the dehumidifying wheel beingregenerated by evaporating the adsorbed moisture to thereby supply theevaporated moisture into the high-temperature outside air in the firstwet channel; and a regenerative-evaporative cooler installed in the drychannel at a position between the circulated air supply hole and thedehumidifying wheel and serving to cool the circulated air in the drychannel, which was dehumidified to high-temperature dry air by thedehumidifying wheel and subsequently, heat exchanged and cooled, thecooled circulated air being delivered to the air supply hole of thecase.

Preferably, the device further comprises a direct-evaporative coolerinstalled in the dry channel at a position in front of theregenerative-evaporative cooler, the direct-evaporative cooler servingto carry out a secondary cooling operation of the circulated airdischarged from the regenerative-evaporative cooler.

Preferably, the device further comprises a first filter installed in thefirst wet channel at a position between the outside air suction hole andthe sensible heat exchanger and serving to remove impurities containedin the outside air.

Preferably, the device further comprises an exhaust blower installed inthe second wet channel at a position between the sensible heat exchangerand the flow hole and serving to forcibly discharge the outside air fromthe second wet channel through the exhaust hole.

Preferably, the device further comprises: a second filter installedbetween the circulated air suction hole and the dehumidifying wheel andserving to remove impurities contained in the circulated air; and an airsupply blower installed between the dehumidifying wheel and theregenerative-evaporative cooler and serving to forcibly discharge thecooled circulated air from the dry channel through the air supply hole,wherein the second filter and the air supply blower are installed in thedry channel.

Preferably, the case further has a cooler exhaust hole provided at thedry channel for discharging high-temperature air generated while theregenerative-evaporative cooler carries out a secondary coolingoperation.

Preferably, the amount of the high-temperature air to be dischargedthrough the cooler exhaust hole is 30% of the total circulated air.

Preferably, the hot water to be introduced into the heating coil isdelivered from any one selected from among a cogeneration plant, aheating boiler, a micro-turbine, a small gas engine, a small gasturbine, a gas boiler, and an oil boiler.

Preferably, the circulated air suctioned through the circulated airsuction hole is mixed with the outside air by a predetermined mixingratio of 7:3.

ADVANTAGEOUS EFFECTS

According to a dehumidifying cooling device for district heating of thepresent invention having the above described configuration, it ispossible to carry out an air cooling operation by use of hot watersupplied by large-scale or small-scale district heating systems and gasor oil boilers installed in individual households. Accordingly, thepresent invention has the effect of achieving a reduced device size viathe implementation of the cooling operation under the atmosphericpressure state, and reducing manufacturing costs by virtue of asimplified system configuration.

DESCRIPTION OF DRAWINGS

The above and other objects, features and other advantages of thepresent invention will be more clearly understood from the followingdetailed description taken in conjunction with the accompanyingdrawings, in which:

FIG. 1 is a view illustrating the configuration of a dehumidifyingcooling device for district heating according to the present invention;

FIG. 2 is a view illustrating the flow of air in the dehumidifyingcooling device for district heating according to the present invention;and

FIG. 3 is a graph illustrating the temperature distribution of humid airused in the dehumidifying cooling device for district heating accordingto the present invention.

BEST MODE

Now, the configuration of a dehumidifying cooling device for districtheating according to the present invention will be described in detailwith reference to the accompanying drawings.

In the following description of the present invention, a detaileddescription of known functions and configurations incorporated hereinwill be omitted when it may make the subject matter of the presentinvention rather unclear. Also, the terms used in the followingdescription are terms defined taking into consideration the functionsobtained in accordance with the present invention. The definitions ofthese terms should be determined based on the whole content of thisspecification because they may be changed in accordance with the optionof a user or operator or a usual practice.

FIG. 1 is a view illustrating the configuration of a dehumidifyingcooling device for district heating according to the present invention.

Referring to FIG. 1, the dehumidifying cooling device 100 according tothe present invention comprises a case 110, a first filter 120, asensible heat exchanger 130, a heating coil 140, a dehumidifying wheel150, an exhaust blower 160, a second filter 170, an air supply blower180, a regenerative-evaporative cooler 190, and a direct-evaporativecooler 200.

The case 110 is made of a metallic material and has a rectangular boxshape. The case 110 is installed with a first partition 113 to dividethe interior of the case 110 into a wet channel 112 and a dry channel111. The case 110 is further installed with a second partition 114 todivide the wet channel 112 into a first wet channel 112-1 and a secondwet channel 112-2. The case 110 has an outside air suction hole 115provided at one end of the first wet channel 112-1 for introducingoutside air into the first wet channel 112-1 and an exhaust hole 116provided at one end of the second wet channel 112-2 for discharging theoutside air. The second partition 114 is perforated with a flow hole114-1 for transferring the outside air from the first wet channel 112-1into the second wet channel 112-2. The case 110 also has a circulatedair suction hole 117 provided at one end of the dry channel 111 forintroducing circulated air from a conditioning space CS into the drychannel 111 and an air supply hole 118 provided at the other end of thedry channel 111 for supplying cooling air into the conditioning spaceCS. The dry channel 111 of the case 110 is further provided with acooler exhaust hole 119 for discharging high-temperature air generatedwhile the regenerative-evaporative cooler 190 carries out a secondarycooling operation that will be described hereinafter. The circulatedair, introduced into the case 110 through the circulated air suctionhole 117, is mixed with the outside air at a ratio of 7:3, to keep theinterior of the case 110 in the atmospheric pressure state.

The first filter 120 is located in the first wet channel 112-1 of thecase 110 at a position between the outside air suction hole 115 and thesensible heat exchanger 130. The first filter 120 is used to removeimpurities contained in the suctioned outside air. Preferably, the firstfilter 120 is an antibacterial filter, and is easily separable from thecase 110.

The sensible heat exchanger 130 has a rotating shaft 131 installed inthe same direction as the second partition 114 and takes the form of adisc to rotate about the rotating shaft 131 inside the first and secondwet channels 112-1 and 112-2 of the case 110. The sensible heatexchanger 130 is used to heat exchange the outside air introduced intothe first wet channel 112-1 through the outside air suction hole 115with the outside air to be discharged from the second whet channel 112-2through the exhaust hole 116. The sensible heat exchanger 130 takes theform of a honeycomb-patterned disc fabricated by processing a thinplate, such as an aluminum plate, etc. suitable for heat exchange. Thereare provided an additional motor and belt (not shown) for rotation ofthe sensible heat exchanger 130.

The heating coil 140 is located in the first wet channel 112-1 of thecase 110 at a position between a rear end of the sensible heat exchanger130 and the flow hole 114-1. The heating coil 140 is used to raise thetemperature of the outside pair passing through the first wet channel112-1 by use of heat of hot water introduced thereinto. The hot waterintroduced into the heating coil 140 is delivered from any one selectedfrom among a cogeneration plant, a heating boiler, a micro-turbine, asmall gas engine, a small gas turbine, a gas boiler, and an oil boiler,and has a temperature within a range of 60 to 120° C.

The dehumidifying wheel 150 has a rotating shaft 151 installed in thesame direction as the first partition 113, and takes the form of a discto rotate about the rotating shaft 151 inside the first wet channel112-1 and the dry channel 111 of the case 110. The dehumidifying wheel150 is located behind the heating coil 140 and serves to adsorb andremove moisture contained in the circulated air within the dry channel111. The dehumidifying wheel 150 is regenerated by evaporating theadsorbed moisture to thereby supply the moisture into thehigh-temperature outside air within the first wet channel 112-1. Thedehumidifying wheel 150 takes the form of a honeycomb-patterned disccontaining an adsorbent, such as silica gel, zeolite, or the like, foradsorbing the moisture contained in the circulated air in a dryadsorption manner. There are provided an additional motor and belt (notshown) for rotation of the dehumidifying wheel 150.

The exhaust blower 160 is installed in the second wet channel 112-2 ofthe case 110 at a position between the sensible heat exchanger 130 andthe flow hole 114-1, and used to forcibly discharge the outside air fromthe second wet channel 112-2 through the exhaust hole 116.

The second filter 170 is installed in the dry channel 111 of the case110 at a position between the circulated air suction hole 117 and thedehumidifying wheel 150 and used to remove impurities and bad smellcontained in the circulated air. Preferably, the second filter 170 is anantibacterial filter, and is easily separable from the case 110.

The air supply blower 180 is installed in the dry channel 111 of thecase 110 at a position between the dehumidifying wheel 150 and thesensible heat exchanger 130 and used to forcibly discharge thecirculated air from the dry channel 111 through the circulated airsupply hole 118.

The regenerative-evaporative cooler 190 is installed in the dry channel111 at a position between the circulated air supply hole 118 and thedehumidifying wheel 150. If the circulated air introduced into the drychannel 111 is dehumidified by the dehumidifying wheel 150 so as to bechanged to high-temperature dry air and subsequently, heat exchanged andcooled, the regenerative-evaporative cooler 190 further cools thecirculated air. The cooled circulated air is delivered to the air supplyhole 118 of the case 110, whereas the high-temperature air generatedduring cooling is delivered to the cooler exhaust hole 119. Here, theamount of the high-temperature air to be discharged through the coolerexhaust hole 119 is 30% of the total circulated air. The interior of theregenerative-evaporative cooler 190 is divided into a dry channel and awet channel. If a part of the air, passing through the dry channel, isdelivered into the wet channel, the air is cooled as water is evaporatedby the high-temperature surface of the wet channel, thereby acting toabsorb heat from the remaining higher temperature air passing throughthe dry channel. Thereby, the air passing through the dry channel can becooled to a dew-point temperature to the maximum extent without anincrease of humidity. The configuration of the regenerative-evaporativecooler is disclosed in Korea Patent Registration No. 0409265 and thus, adetailed description thereof will be omitted herein.

The direct-evaporative cooler 200 is installed in the dry channel 111 ofthe case 110 at a position in front of the regenerative-evaporativecooler 190. The direct-evaporative cooler 200 serves to carry out asecondary cooling operation of the circulated air from theregenerative-evaporative cooler 190, so as to supply the resulting airinto the conditioning space CS through the air supply hole 118 of thecase 110.

Hereinafter, the operation and effects of the dehumidifying coolingdevice for district heating according to the present invention will bedescribed in detail with reference to FIGS. 1 to 3.

FIG. 2 is a view illustrating the flow of air in the dehumidifyingcooling device for district heating according to the present invention,and FIG. 3 is a graph illustrating the temperature distribution of humidair used in the dehumidifying cooling device.

Explaining first a dehumidifying cooling operation carried out in thedry channel 111, circulated air from the conditioning space CS, which ismixed with high-temperature and high-humidity outside air, is introducedinto case 110 through the circulated air suction hole 117 under theoperation of the air supply blower 180. After passing through the secondfilter 170, the introduced circulated air sequentially passes throughthe dehumidifying wheel 150 such that the moisture contained in thecirculated air is removed by the adsorbent.

The dehumidified circulated air is heated by adsorptive heat generatedfrom the surface of the dehumidifying wheel 150. The resultinghigh-temperature and low-humidity circulated air passes through theregenerative-evaporative cooler 190.

If the circulated air is introduced into the regenerative-evaporativecooler 190, 70% of the circulated air is cooled while passing throughthe regenerative-evaporative cooler 190, and 30% of the circulated airis discharged to the outside through the cooler exhaust hole 119.

The circulated air, having passed through the regenerative-evaporativecooler 190, is secondarily cooled while passing through thedirect-evaporative cooler 200, thereby being supplied into theconditioning space CS through the air supply hole 118 of the case 110.

Next, explaining a heat-exchange operation carried out in the wetchannel, high-temperature and high-humidity outside air is introducedinto the first wet channel 112-1 through the outside air suction hole115 and passes through the first filter 120 under the operation of theexhaust blower 160. Then, the filtered outside air is heat exchangedwith the high-temperature and high-humidity outside air in the secondwet channel 112-2 while passing through the sensible heat exchanger 130.Thereby, the outside air with the raised temperature passes through theheating coil 140.

While passing through the heating coil 140, the temperature of theoutside air is further raised by hot water supplied into the heatingcoil 140. Thereby, the outside air to be delivered into thedehumidifying wheel 150 has a significantly raised temperature.

Then, while passing through the dehumidifying wheel 150 rotating in astate of adsorbing moisture therein, the outside air forcibly evaporatesmoisture thereof. Thereafter, the dehumidified outside air is moved intothe second wet channel 112-2 through the flow hole 114-1. Through theabove described process, the surface of the dehumidifying wheel 150 isreturned to an original dried state thereof, thereby recovering adehumidifying ability thereof.

The high-temperature and high-humidity outside air, moved into thesecond wet channel 112-2, is heat exchanged with the outside air in thefirst wet channel 112-2 while passing through the sensible heatexchanger 130, and discharged to the outside through the exhaust hole116.

Referring to FIGS. 2 and 3, in the dehumidifying cooling device fordistrict heating according to the present invention, if circulated air{circle around (1)} is introduced into the case, the circulated air{circle around (1)} is mixed with outside air {circle around (7)}, toproduce mixed air {circle around (2)} having a raised temperature andabsolute humidity. While passing through the dehumidifying wheel, themixed air {circle around (2)} is changed to higher-temperature and lowerabsolute-humidity air {circle around (3)}.

Then, the air {circle around (3)} is heat exchanged to produce air{circle around (4)} having a rapid drop only in temperature. Insequence, while passing through the regenerative-evaporative cooler, thetemperature of the air {circle around (4)} is changed into air {circlearound (5)} having a slightly lowered temperature and slightly raisedabsolute humidity.

Meanwhile, when the introduced outside air {circle around (7)} passesthrough the first filter, the filtered air {circle around (8)} has thesame temperature and absolute humidity as those of the air {circlearound (7)}. The air {circle around (8)} is heat exchanged with theoutside air {circle around (11)} in the first wet channel while passingthrough the sensible heat exchanger. The resulting heat exchanged air{circle around (9)} is slightly raised in temperature, but keeps thesame absolute humidity as that of the air {circle around (8)}. Then, theair {circle around (9)} is raised only in temperature while passingthrough the heating coil, resulting in high-temperature air {circlearound (10)}.

The air {circle around (10)} is dropped in temperature, but raised inabsolute humidity in the course of passing through the dehumidifyingwheel, thereby being changed to low-temperature and high-humidity air{circle around (11)}. Then, while passing through the sensible heatexchanger in the second wet channel, the air {circle around (11)} isheat exchanged with the outside air {circle around (8)} in the first wetchannel such that the heat exchanged air {circle around (12)}, which isslightly dropped in temperature but keeps the same absolute humidity asthe air {circle around (11)}, is discharged through the exhaust hole.

In conclusion, in the dehumidifying cooling device for district heatingaccording to the present invention, air to be supplied into aconditioning indoor space is subjected to the transfer of heat andmoisture via a direct contact with the dehumidifying cooling device.This has the effect of achieving excellent transfer efficiency andproducing and supplying cooling air with a low-temperature heatingsource of 60° C. Further, differently from conventional absorptivedevices, the dehumidifying cooling device is operable in the atmosphericpressure state and has a simplified configuration, resulting in aconsiderable reduction of manufacturing costs.

INDUSTRIAL APPLICABILITY

As apparent from the above description, a dehumidifying and coolingdevice according to the present invention can be installed toresidential and business buildings, etc. using hot water delivered bydistrict heating facilities, so as to utilize the hot water as a sourcefor cooling a room.

Although the preferred embodiments of the present invention have beendisclosed for illustrative purposes, those skilled in the art willappreciate that various modifications, additions and substitutions arepossible, without departing from the scope and spirit of the inventionas disclosed in the accompanying claims.

1. A dehumidifying cooling device for district heating comprising: acase having a first partition to divide the interior of the case into awet channel and a dry channel and a second partition to divide the wetchannel into a first wet channel and a second wet channel, the first wetchannel being provided at one end thereof with an outside air suctionhole for introducing outside air into the first wet channel, the secondwet channel being provided at one end thereof with an exhaust hole fordischarging the outside air, the second partition being perforated witha flow hole for transferring the outside air from the first wet channelinto the second wet channel, the dry channel being provided, at one endthereof, with a circulated air suction hole for introducing circulatedair from a conditioning space into the dry channel and, at the other endthereof, with an air supply hole for supplying cooling air into theconditioning space, a sensible heat exchanger configured to rotate aboutthe second partition and serving to heat exchange the outside air,introduced into the first wet channel through the outside air suctionhole, with the outside air to be discharged from the second wet channel;a heating coil installed in the second wet channel at a position betweena rear end of the sensible heat exchanger and the flow hole and servingto raise the temperature of the outside air passing through the secondwet channel by use of heat of hot water introduced into the heatingcoil; a dehumidifying wheel configured to rotate about the firstpartition at a position between a rear end of the heating coil and theflow hole and serving to adsorb and remove moisture contained in thecirculated air within the dry channel, the dehumidifying wheel beingregenerated by evaporating the adsorbed moisture to thereby supply theevaporated moisture into the high-temperature outside air in the firstwet channel; and a regenerative-evaporative cooler installed in the drychannel at a position between the circulated air supply hole and thedehumidifying wheel and serving to cool the circulated air in the drychannel, which was dehumidified into high-temperature dry air by thedehumidifying wheel and subsequently, heat exchanged and cooled, thecooled circulated air being delivered to the air supply hole of thecase.
 2. The device according to claim 1, further comprising: adirect-evaporative cooler installed in the dry channel at a position infront of the regenerative-evaporative cooler, the direct-evaporativecooler serving to carry out a secondary cooling operation of thecirculated air discharged from the regenerative-evaporative cooler. 3.The device according to claim 1, further comprising: a first filterinstalled in the first wet channel at a position between the outside airsuction hole and the sensible heat exchanger and serving to removeimpurities contained in the outside air.
 4. The device according toclaim 1, further comprising: an exhaust blower installed in the secondwet channel at a position between the sensible heat exchanger and theflow hole and serving to forcibly discharge the outside air from thesecond wet channel through the exhaust hole.
 5. The device according toclaim 1, further comprising: a second filter installed between thecirculated air suction hole and the dehumidifying wheel and serving toremove impurities contained in the circulated air; and an air supplyblower installed between the dehumidifying wheel and theregenerative-evaporative cooler and serving to forcibly discharge thecooled circulated air from the dry channel through the air supply hole,wherein the second filter and the air supply blower are installed thedry channel.
 6. The device according to claim 1, wherein the casefurther has a cooler exhaust hole provided at the dry channel fordischarging high-temperature air generated while theregenerative-evaporative cooler carried out a secondary coolingoperation.
 7. The device according to claim 6, wherein the amount of thehigh-temperature air to be discharged through the cooler exhaust hole is30% of the total circulated air.
 8. The device according to claim 1,wherein the hot water to be introduced into the heating coil isdelivered from any one selected from among a cogeneration plant, aheating boiler, a micro-turbine, a small gas engine, a small gasturbine, a gas boiler, and an oil boiler.
 9. The device according toclaim 1, wherein the circulated air suctioned through the circulated airsuction hole is mixed with the outside air by a predetermined mixingratio.
 10. The device according to claim 1, wherein the predeterminedmixing ratio of the circulated air to the outside air is 7:3.